Integrating mechanism



J.F. SHANNON 2,877,669 INTEGRATING MECHANISM Fil'd April so. 1953 mmvrmJACK F. SHANNON Clack F. Shannon, Euclid, Bhio,

".be made of a time length structure.

United States Patent 2,877,669 INTEGRATING MECHAYISM assignor to BaileyMeter a corporation of Delaware Application April 39, 1953, Serial No.352,172 5 Claims. (Cl. 74789) Company,

This invention relates to improvements in mechanisms "for theintegration of variables, especially mechanisms for integratingvariables with respect to time, and where such variables may be of aphysical, chemical, electrical, hydraulic or other nature.

This invention also relates to driving means for the mechanism forintegrating variables wherein the basic source of'power for the drivingmechanism is a fluid pressure.

This invention is. specifically an improvement of that type ofintegrator disclosed and claimed in the patent to Gorrie 1,892,133. TheGorrie device was compared, in its specification, with integrators ofthe planimeter, or friction contact, type wherein the speed of operationof the register is varied in accordance with the value of the variable,while the operation of the register is continuous. Gorrie declared, onthis basis, that it was known to obtain a total over any period of time,.or. integrate a variable with respect to time by periodic determinationof the value ofthe variable, with a movement or" the register beingproportional then suggested the to the value of the variable. Gorrievalue of the variable be determined at magnitude of the increments ofmovement of the register which is the percentage of the time periodproportional to the value of the variable.

The Gorrie type of integrator comprises an arrangementwhereinpredetermined time intervals are chosen and the driving means for theregister operated at a constant speed but without the value of thevariable at a particular instant during the time interval being thedetermining factor of the amount of actuation of the register during thetime interval. Actually, the Gorrie type of" integrator employs a systemwherein the length of "actuation of the register during each interval oftime chosen is in accordance with the value of the variable at aparticular instant during that time interval, modified by the value ofthe variable throughout the actuation. In general, this is accomplishedby allowing the value of the variable to change during that time orthrough that part of the interval of time wherein the register isactuated.

'In an application S. N. 235,736, filed May '2, 1952, by Jack F. Shannonand Randall C. Aberegg, now (Patent 2,690,871, the problem of providinga consistent mode of starting the integrating portion of the cycle inthe Gorrie type of integrator was met with a specific The approach inthis Shannon et a1. applica- .'.tion was novel and effective inproviding the desired function. However, certain dimensional limitationsin commercial embodiments of this inventive concept have caused thepresent applicant to seek other structural solutions to the basicproblem.

It should be noted that the dominating structure of fthe-Gorrieintegrator is the toothed, escapement wheel which is engaged by the pawlpositioned by cooperation between the meter mechanism and theconstant-rise cam "drivenby the constant-speed source of power for the"some point of time within the period or interval, and the i 2,877,669v, Patented Mar. 17, 195.9

integrator. 'Ifthe pawl must be engaged with the wheel teeth sopositively that the disengaging force exerted by the pin positioned bythe meter mechanism flexes, or bonds, the pawl arm in forcing thedisengagement, a

The basic problem will be appreciated, therefore, as one of reducing thetorque on this escapement wheel so that its engagement will be confinedsolely to the influence of the variable integrated.

Both the Gorrie patent and the Shannonet al. application disclosure makeit clearthat their source of constant speed is inherently arranged todrive the integrator register through a friction clutch whichrnust beadjusted to meet the highest power requirements for turning the registermechanism. The mechanical arresting mechanism including the escapementwheel is very simple. The wheel iscarried directly on the register shaftso that when engaged by the pawl the register is stopped. But thefriction clutch between the'source of constant speed and the registershaft then develops the undesirably high torque directly on theescapement wheel.

The Shannon et a1. application disclosed a relief pawl which functionedduring the interval of escapement wheel -arrestment to reverse therotation of the wheel a conspite the high torque on the escapementwheel. Thus the torque on the escapement wheel was not reduced by theShannon et a1. mechanism, but its effect was overcome by an additionalpawl.

The present invention is directed to the fundamental approach of torquereduction on the escapement wheel structure of the Gorrie integrator. Ingeneral, the principle of mechanical gear differential structure hasbeen utilized in the present invention to make the development of a hightorque by the source of constant speed unnecessary. By control of adifferential between the power shaft and register shaft with theescapement wheel, little more torque than the highest drivingrequirements of the register need be developed. This novel structure isadaptable to the Gorrie type of integrator as the addition of structureon the central shaft of the device takes less bulk than the provision ofadditional pivot points for structure such as the relief pawl of theShannon et al. application.

Precisely the forms given the embodiments of the invention will bedepicted in detail in the following description of the various drawingfigures. The prime objective, of the invention, however, is theimprovement of the Gorrietype of integrator by reduction of the powerneeded from the source of constant speed.

Other novelty in the disclosure of this application is found in thestructure for supplying the source of constant speed. It is, of course,recognized that electric motors are the more conventional source ofpower for these mechanisms. However, there are some. applications wherethe use of electric power is precluded (because of safety measures. Toprovide for these applications, the present invention advances a unique,,fluidpower mechanism which delivers sufiicient power for. the servicerequired and at a constant rate. With the power requirements reduced,not only are relatively low-powered, fluid-actuated mechanisms feasiblein this service, but spring-actuatedmechanisms may be also satisfactory.

It should be appreciated that a'start toward conception of this powermechanism begins with some form of entable novelty depends. ,niquesdictate the species which lends itself more readily to production.

fluid turbine. The present disclosure illustrates the use of an airnozzle against the impeller blades of a simple turbine which is gearedtodeliver sufficient power to op- -erate the integrating mechanism. Theuniqueness of ,thisspecific structure disclosed lies in the combination,of this fluid turbine, gears and a mechanism for metering the poweravailable to the integrating mechanism at" a ture is centered about aspring member attached to a Ishaft of the gear train and loaded from theescapement mechanism in order to provide aregulation of the force.-.transmitted to the integrator.

It may now be appreciated that another object of the invention is toprovide an improved fiuid pressure mecha- .nism for maintaining asourceof constant speed for the ;working shaft of a mechanism absorbingor transmitting that power.

Another object of the invention is to provide a differ- ?ential drivefor the escapement type of integrator which is compact, easilymanufactured, requires substantially no maintenance and improves theaccuracy of the integration.

In the drawings:

Fig. l is an isometric and diagrammatic representation, with partialexplosion, of the invention in connection with'an escapement type ofintegrator responsive to .a variable.

Fig. 2 shows apartially cross sectioned side elevation of the inventionof Fig. l. r

Fig. 3 shows a partially cross-sectioned side elevation of another formof the invention disclosed at Fig. 1.

Fig. 4 shows a partially crosssectioned side elevation i of another formof the inventiondisclosed at Fig. 1.

The disclosure of the drawings covers a complete integrating mechanismas driven by a source of power at a constant rate. The driving means, orsource of power,

has a novel arrangement of structure which will be subsequentlydescribed. However, as the ultimate function .of the source of power iswell established, the disclosure will he basically directed to thestructural novelty of the escapement mechanism driving the register.

There are several variations of the escapement mechanism, all embodyingthe basic concept upon which pat- Present manufacturing tech- However,as manufacturing techniques change it is entirely possible that any oneof the embodlments shown will be adopted by a specific manufacturer whotakes advantage of this disclosure.

The species of the invention preferred for Figs. 1 and 2was selectedbecause of the clarity with which it lends itself to illustration.

The alternate arrangements of Figs 3 and 4 are easily understood, froman initial understanding of the arrangement of Figs. 1 and 2. Each ofthe arrangements of Figs. 3 and 4 may be substituted for that of Fig. lin combination with the source of power illustrated. Common numeraldesignations, on the characteristic cam and escapement wheel, have beenused to emphasize this interchangeability, as well as the input andoutput gear members of this section of the combination.

The structure of the invention disclosed lends itself :rather well todiscussion in sections without impairing illustration of the unity andcooperation between the sect1ons.

I will first discuss the structure specifically designated by numerals1- -12 inclusive. A mechanism (not disclosed) is responsive to aquantitative variable to be integrated with respect to time to determinethe total, "or cumulative, quantity of the variable during a specificinterval of time. What has been disclosed in Fig. l is a variable link 1which is responsive to the undisclosed 4 mechanism. The variable link 1will be caused to take up vertical positions over a range, indicative ofthe instantaneous value of the variable. To produce ultimately desiredmotions, variable link 1 is caused to rotate a variable link arm 2 whichin turn rotates a shaft 3 in accordance with the variable. It is thenpossible to rigidly attach an indicating pointer 4 to shaft 3 and thispointer will then cooperate with exhibiting scale 5 for giving visualrepresentation of the variable. A chart, moving with time, may besubstituted for scale 5 and a recording pen may be substituted forpointer 4 to cooperate with the chart and give a permanent andcontinuous record with respect to time.

The indicating and/or recording of the variable magnitude, in thisparticular instance, is an incidental function of the disclosedstructure. Fundamentally, the variably rotated shaft 3 has attached toit a pivot positioning beam 6 which carries variably positioned pivot 7through 'an are about the axis of shaft 3 over the normal range ofpositions representative of the variable. The variable pivot 7 is at oneend of an integrating pin beam 8 whose opposite end carries a roller 9whose vertical position be-. tween two limits in space is determined bythe main cam of the integrating mechanism. With one end. of beam 8positioned by the variable and the other end of beam 8 positioned inaccordance with a predetermined program, integrating pin 10, carried atan intermediate point on the beam 8, is caused to actuate pawl 11 aboutpawl pivot 12 for periodic engagement of the escapement wheel of theintegrator and so regulate the actuation of the register which exhibitsthe quantitative total, or integration, of

v the variable.

tice of this structure, provision will be made for giving relativeadjustments of integrating pin 10 on integrating pin beam 8 as well asadjustments to the position in space of pawl pivot 12. These adjustmentsare necessary for purposes of calibration but would be rather incidentaldisclosure here.

The structure disclosed thus far cooperates to engag the escapementwheel of the integrator with pawl 11 for periods representative of thevalue of the variable integrated. In general, a register with graduateddials, for afiording a continuously available means of reading theaccumulated total of the variable for a desired time interval iscontrolled by rotation of the escapement wheel. Actuation of thisregister is accomplished, through the novel arrangement of the presentinvention, from the mechanism of the integrator whose escapement wheelis controlled by engagement with pawl 11.

As the escapement wheel and/or cam is to be rotated at a constant speed,it is now well to turn tostructure provided for giving this rotation.Here, again, a group of structures of the present disclosure may beconsidered as a unit without obscuring the cooperation with theremainder of the disclosed structure.

Beginning with the impeller turbine 20, it is easily understood how ablast of fluid from nozzle 21 will impinge upon the vanes of turbine 20and rotatethe turbine shaft 22. All of the gears and shafts of thisstructure 2034 inclusive have been depicted diagrammatically withoutdetracting from the clarity of the function of the structure.

On turbine shaft 22 there is mounted turbine shaft gear 23 which is oneend of a train of gears mounted on shafts 24 and 25. Output shaft gear26 represents the end of this gear train and it is from this outputshaft gear 26 that power is delivered to the integrating mechanismcontrolled by the escapement wheel 28. Of course there are designconsiderations involved which may call for additional intermediateshafts such as depicted by 24 with gears in the train from gear 23 togear 26. These considerations include the power available from turbineshaft 22 and required at output shaft gear 26.

The present invention has provided an escapement mechanism generallyindicated at 27, which is characterized by a conventional escapementwheel 28 whose shaft 29 has a gear mounted thereon as one end of a traincooperating with other gears mounted on intermediate shafts representedby 30 and terminating with regulating gear 31. In common with similarescapement mechanism, the structure of 27 is arranged to control wheel28 so that shaft 29 will turn at a predetermined rate.

Shaft 29 will not turn continuously because the escapement mechanisminherently interrupts the rotation in one direction. Nevertheless, theintermittent rotation in the one direction proceeds at an average rateheld constant by the escapement mechanism 27.

The rotation of regulating gear 31 is in the same direction as that ofshaft 25. However, whereas the rotation of shaft 25 is directly underthe control of turbine 20, the rotation of regulating gear 31 is underthe control of escapement mechanism 27. It is contemplated thatvariations will occur in the fluid supplied nozzle 21, impinging on thevanes of turbine 20. Consequently, if the available power from turbine20 were elevated above the requirements at output shaft gear 26, itwould be desirable to throttle this available power by regulating gear31 so that fluctuations from turbine 20 would be isolated from outputshaft gear 26.

The present invention provides a regulating shaft 32 on which regulatinggear 31 is mounted andregulating spring housing 33 connected to outputshaft '25 through regulating spring 34. Obviously, shaft 32 is tubularand output shaft 25 extends therethrouh for connection with the innerend of the coil of spring 34. The outer end of spring 34 is simplyattached to spring housing 33 and the differential between the poweravailable from turbine 20 and that required at output shaft gear 26 isstored in spring 34.

This arrangement solves two basic problems. First it solves the problemof providing a regulated rotation of output shaft 25. Secondly, itsolves the problem of preventing the intermittent action of theescapement mechanism 27 from being transmitted to output shaft 25. Therocking motion of escapement wheel 28, transmitted directly to shaft 32is absorbed by the resiliency of spring 34.

A source of constant speed has now been provided for the structure,centering about the cam and escapement wheel of the integrator. Thepower from this source is available at output shaft gear 26 and is takendirectly to the integrator cam 42 through input gear 40 mounted on camshaft 41, both of which are diagrammatically depicted in Fig. 1. Cam 42of the integrator is fixed to this shaft 41 in all of the variousarrangements of the invention disclosed. However, shaft 41 may actuate adifferent structure of the invention, dependent upon which species isbeing considered. Integrator escapement wheel 43 also controls, and isactuated by, different arrangements in the various species disclosed,but whatever the arrangements otherwise, an output gear 44 is providedto drive shaft 45 of register 46. All of this structure 40-46 is commonwith the various species of the invention disclosed and may be taken asa common denominator to illustrate their basic interchangeability.

Taking cam 42, in its connection to shaft 41 as driven by input gear 40,its function can be disposed of by reference to the basic Gorrie patent.This cam 42 is shaped to give a rise and fall to roller 9 at a uniformrate be tween two predetermined limits in space. This function is abasic requirement for this type of integrator and need not be discussedin more detail.

Taking the arrangement of Fig. l, specifically, it is to be understoodthat cam shaft 41 has been broken in order to give clear illustration tothe driving mechanism between escapement wheel 43 and output gear 44. Aspider plate 47 has been fixed to cam shaft 41 so that, in thisembodiment of Fig. l, cam 42 and spider plate 47 turn together.

Pinion gears 48 and 49 are now to be considered, as their connectingshaft 50 is carried by spider plate 47. Pinion gear 48 is directlymeshed with a gear turned by escapement wheel 43 and may, therefore, bereferred to as the escapement pinion. Pinion 49 is meshed directly witha gear carried on the same shaft as output gear 44 and may, therefore,be referred to as the output pinion. These pinion gears, connected byshaft 50, may rotate in the hole in spider plate 47 provided for shaft50 as well as execute a planetary motion about the axis of retation ofspider plate 47. To provide a desired function at a certain period inthe operation of these parts, a constant friction member 51 is providedon the shaft of output gear 44.

In order to prevent any confusion whatsoever as to the relationships ofthese structures 40--51, Fig. 2 has been provided as a partiallycross-sectioned side elevation of this same structure depicted inperspective in Fig. l. The operation of this structure centers aboutrotation of shaft 41. If the escapement wheel 43 is free of pawl 11,spider 47 will impart a planetary motion to pinion gears 48 and 49 aboutthe axis of rotation of shaft 41 while constant friction means 51 willprevent rotation of output gear 44 and, consequently, actuation ofregister 46. In order to transmit power through a differential withpinion gears having rotation about an axis parallel with that aboutwhich they describe a planetary motion, the pinion gears must have adifferential in size. The exact differential in size will depend uponthe speed desired for escapement wheel 43 when released and the speeddesired for register 46 when escapement wheel 43 is engaged by pawl 11.

As specifically disclosed in Figs. 1 and 2, when escapement wheel 43 isengaged by pawl 11, the peripheral speed of the gear teeth of escapementpinion 48 is to be noted as less than that of the gear teeth on outputpinion gear 49. Therefore, the gears meshing with these pinions willrotate at differential speeds and actuate register 46. When pawl 11 doesnot engage escapement wheel 43 constant friction 51 will prevent anyfriction from the gears rotating the shaft of output gear 44, and outputpinion gear 49 will be noted as having a speed of rotation greater thanthe gear attached to escapement wheel 43 which meshes with escapementpinion gear 48. Escapement wheel 43 will then be driven in a directionopposite to the rotation of spider plate 47.

Returning to the basic objective of the present invention, it must beappreciated that" this arrangement reduces the torque on escapementwheel 43 as compared with the prior arrangements wherein a frictionclutch directly connected the escapement wheel to the cam shaft. Thisdriving of the escapement wheel 43 through the differential dominated bypinion gears 48 and 49 in spider 47 eliminates the necessity ofproviding power equal to the highest register requirement plus thatnecessary to overcome the friction coupling between the source ofconstant rotation and the escapement wheel in the Gorrie type ofintegrator. The results obtain the objective of the invention in that,with the torque greatly reduced on escapement wheel 43, thedisengagement from the teeth thereof by pawl 11 gives no disturbingreaction back through the linkage to a manifesting member such aspointer 4. Engagement and disengagement of the pawl 11 from the teeth ofescapement wheel 43 follows more precisely the change of the variablebecause of the elimination of the disturbance due to the high torque onthe escapement wheel.

Going now to Fig. 3, it must be initially appreciated that thisarrangement is based about the establishment of a fixed, central shaft60. Input gear 40, cam shaft 41,. cam 42, escapement wheel 43 and outputgear 44 have the same basic identity and function as in the precedingfigures. However, cam shaft 41 is now tubular and arranged to rotateabout stationary shaft 60 under the control of input gear 40. Althoughtubular shaft 41 also carries cam 42 it does not now carry a spider asin the first two figures but terminates in a beveled gear in thedifferential structure. Output gear 44 is now provided with a tubularshaft 61 which rotates about stationary shaft 60 and extends back intothe differential to connect with a spider plate 62 in which rotates thepinion gears 63 and 64. The escapement wheel 43 is also provided with atubular shaft which accommodates output shaft 61 in order to extend agear 65 back into the differential. The cam shaft gear 66, the twopinion gears 63 and 64 and the escapemeut gear 65 comprise thedifierential, with spider plate 62. having a fixed friction member 67applied thereto after the fashion of member 51 in the precedingdisclosure.

The cooperation of this structure of Fig. 3 is basically the same as thepreceding disclosure in obtaining the improved results of the invention.Arrestment of escapement wheel 43 will cause cam shaft gear 66 to bothrotate and impart a planetary motion topinion gears 63 and 64 againstthe constant friction member 67, to drive spider plate 62 and attachedoutput shaft 61 in actuation of register 46. It is again emphasized thatthe force needed to arrest escapement wheel 43 is relatively smallcompared to the prior arrangements wherein the escapement wheel wasvconnected through a friction clutch di rectly to cam shaft41.

When. escapement wheel 43 is released from engagemerit. with pawl 11,friction member 67 prevents rotation of spider plate 62v and piniongears 63 and 64 merely rotate in transmitting the power from cam shaf tgear 66 to escapernent gear 65.

Going now to Fig. 4, the common denominator of structure between thisfigure and that of the foregoing disclosure, particularly Fig. 3, iseasily located. Stationary shaft 60 is arranged 'as in Fig. 3, with camshaft 41 and output shaft 61 arranged to slip over and turn. on shaft60. Cam 42, escapement wheel 43, as well as input. gear 40 and outputgear 44, are exactly as delineated in all. of the foregoing disclosure.The central distinction between Fig. 4 and the foregoing figures lies inthe attachment ofescapement wheel 43 to the differential gearing throughthe agency of the pinion gear 81, which may be referred to as an idlergear in this particular arrangement.

Esc'apement wheel 43. has a shaft member 80 attached thereto whichrevolves about stationary shaft 60 and between cam shaft 41 and outputshaft 61. This escapement wheel shaft 80 supports pinion gear 81 aspaced distance from the center of rotation in order that a gear onoutput shaft 61 may be meshed between gear 81 and stationary shaft 60.Meshed with the teeth of gear 81 a greater distance from shaft 60 arethe teeth of a gear carried by cam shaft 41. It might be said that thethree gears form their differential by meshing in a plane normal totheir axis of rotation about stationary shaft 6%. The accommodation oncam shaft 41 for its gear and theform given to escapement wheel shaft 80are a little difficult to follow, but sufficient sectioning has beentaken through this view of Fig. 4 to show the cooperation of the variouscomponents. I

The constant friction device 32 has a function common: with that of 51and. 67 in the preceding figures. Essentially, this device. is to exerta constant, frictional dragonoutput shaft 61. InFig. 4 this deviceis'included' on. the shaft andexertsits friction on stationary shaft 60.In the. preceding Fig. 3, the friction was seemingly easier to apply tothe spider plate 62. However, the functionof this device is theprevention. of rotation by output gear closure.

which causes a transmission of power from shaft 41 to shaft 61. Ofcourse the direction of rotation of the shafts are opposite. As in thepreceding disclosure, the funda mental objective of the invention inreduction of torque on escapement wheel 43 is carried out as before.

What I claim as new and desire to secure by Letters Patent of the UnitedStates, is:

1. In an integrator including an escapement type of movement and havinga register driven thereby, the combination comprising a stationaryshaft, a tubular cam shaft rotating on one end portion of the stationaryshaft, an external gear on the tubular cam shaft for rotating the same,the inner end of the tubular cam shaft being enlarged to provide anopen-ended cylindrical housing for mation provided with gear teeth onits inner periphery and having an operating plate cam extendingoutwardly thereof, a tubular output shaft mounted on the other endportion of the stationary shaft and having an enlarged inner end sleeveportion extending within said internal gear teeth in spaced relationthereto and to the station ary shaft and provided with external gearteeth in opposed spaced relation to said inner periphery gear teeth, apinion gear in operating relation between said inner periphery gearteeth and said external gear teeth, a sleeve flanged. at. one end androtatably mounted on the sta tionary shaft, means for periodicallylocking and releasing said sleeve for predetermined increments of time,a stub shaft mounted in perpendicular relation on the flanged portion ofthe last-mentioned sleeve and rotatably supporting the pinion gear, andan output gear on the other end of said tubular output shaft.

2. The combination of claim 1 in which a friction device is interposedbetween the tubular output shaft and the stationary shaft to exert africtional drag on the lastmentioned shaft.

3. In an integrator including an escapement type of nating in a piniongear and rotatably mounted on the second tubular shaft, means forperiodically locking and releasing said escapement wheel forpredetermined increments of time, an annular spider plate encircling thesaid pinion gears, and a pinion gear rotatably mounted on the innerperiphery of said spider plate meshing with the other two pinion gears.

4. in an integrator including an escapement typeof.

movement and having a register driven thereby, the com binationcomprising a stationary shaft, a first tubular shaft rotating on one endportion of the stationary shaft and having an external input gear fixedthereon, a second tubular shaft rotating on the other end portion of theSta-- tionary shaft and having an external output gear fixed thereon, adifferential gear trainincludinga pinion gear interposed in engagedrelation between a spaced pair. oft

opposed gears, one of which is on the first tubular shaft- -ried by thespider plate formationaud meansfor period--- ically locking said spiderplate against rotation for predetermined increments of time.

5. The combination of claim 4 in which a friction device acts betweenthe second tubular shaft and the stationary shaft to cause rotation ofthe spider plate except when restrained against rotation by said lockingmeans.

References Cited in the file of this patent UNITED STATES PATENTS 10Ross Feb. 2, 1943 Young Mar. 18, 1947 King July 10, 1951 Shannon et al.Oct. 5, 7954 FOREIGN PATENTS France July 21, 1931 France Apr. 11, 1951France Oct. 10, 1951 Germany Sept. 17, 1943 Germany May 11, 1953 GreatBritain July 11, 1929 Great Britain Dec. 12, 1951

